KR101348891B1

KR101348891B1 - A compressor

Info

Publication number: KR101348891B1
Application number: KR20100056735A
Authority: KR
Inventors: 손은기; 윤제수; 안준철; 안희훈
Original assignee: 한라비스테온공조 주식회사
Priority date: 2010-06-15
Filing date: 2010-06-15
Publication date: 2014-01-07
Also published as: KR20110136613A

Abstract

The present invention is to prevent the leakage of the refrigerant between the discharge chamber 154 and the suction chamber 152 in the portion corresponding to the cylinder bore 112 in the compressor. The compressor of the present invention includes: a cylinder block (110) in which a plurality of cylinder bores (112) are arranged in a circle; A rear housing 150 coupled to the rear of the cylinder block 110 and having a suction chamber 152 and a discharge chamber 154 separated by a partition wall 155 in an area of the cylinder bore 112; And a valve assembly 170 interposed between the rear housing 150 and the cylinder block 110 to move the refrigerant between the suction chamber and the discharge chamber and the cylinder bore based on the pressure difference. A sealing groove 155a is formed at an end of the partition wall, and a sealing ring 156 that contacts the valve assembly 170 is mounted on the sealing groove 155a. The sealing ring 156 may be in close contact with the valve assembly to maintain a sufficient surface pressure to prevent leakage of the refrigerant.

Description

Compressor

The present invention relates to a compressor, and more particularly, to a compressor configured to suppress the leakage of the working fluid to be compressed as much as possible to compress the working fluid more efficiently.

First, the configuration of a variable displacement swash plate compressor will be described with reference to FIG.

As shown in FIG. 1, a variable displacement swash plate type compressor (hereinafter also referred to as a "compressor") includes a cylinder block 10 having a plurality of cylinder bores 11 and a front of the cylinder block 10. The front housing 30 is coupled to form the crank chamber 31, and the rear housing 50 is coupled to the rear of the cylinder block 10 to form the suction chamber 51 and the discharge chamber 53. It is included.

The cylinder block 10 is formed with a plurality of cylinder bores 11 for the compression of the refrigerant radially. The cylinder bores 11 are arranged at regular intervals along the outer edge of the cylinder block 10, and are substantially formed through the cylinder block 10. In addition, the pistons 14 are respectively installed inside the cylinder bore 11 to compress the refrigerant in the cylinder bore 11 while linearly reciprocating.

And the front housing 30 is coupled to one side, that is, the front of the cylinder block 10. The rear side of the front housing 30 is formed concave, it is combined with the cylinder block 10 to form a crank chamber 31 therebetween. Mechanisms for reciprocating the piston 14 are provided inside the crank chamber 31.

In addition, the rear housing 50 is coupled to the other side of the cylinder block 10, that is, the rear side. The rear housing 50 is formed with the front face open, is coupled to the cylinder block 10, the suction chamber 51 to suck the refrigerant into the cylinder bore 11, and in the cylinder bore 11 A discharge chamber 53 through which the compressed refrigerant is discharged is formed. Between the cylinder block 10 and the rear housing 50, the suction chamber 51 and the discharge chamber 53 are formed, while the cylinder bore 11 and the suction chamber 51 and the discharge chamber 53 are formed. A valve assembly 70 is provided for interrupting the flow of refrigerant.

The suction chamber 51 is a portion for supplying a refrigerant to be compressed into the cylinder bore 11, and the cylinder block 10 of the rear housing 50 of the portion corresponding to the cylinder bore 11. It is formed at the part corresponding to the center of the face facing.

After the discharge chamber 53 is supplied into the cylinder bore 11 through the suction chamber 51 and the compressed refrigerant is discharged, the rear housing 50 of the portion corresponding to the cylinder bore 11 is discharged. In the radially outward portion is formed. The compressed refrigerant coming out of the discharge chamber 53 is supplied to a heat exchanger for air conditioning required by an automobile.

The suction chamber 51 and the discharge chamber 53 are respectively in communication with the cylinder bore 11 by the pressure difference with the cylinder bore 11 to move the refrigerant. At this time, the valve assembly 70 intercepts the flow of the refrigerant based on the pressure difference between the cylinder bore 11, the suction chamber 51, and the discharge chamber 53.

The driving source for operating the piston 14 is the driving force transmitted from the engine of the vehicle. The driving force in the engine is transmitted to the drive shaft 20 through the pulley P to rotate the drive shaft 20. The drive shaft 20 is coupled to the center bore 16 formed in the center of the cylinder block 10 through the shaft hole 32 of the front housing 30, rotatable based on the rotational force transmitted from the engine Is supported.

Inside the crank chamber 31, a substantially disk-shaped rotor 22 is provided in which the drive shaft 20 is coupled to and fixed to the center thereof. The rotor 22 rotates along the rotation of the drive shaft 20. A hinge arm 24 protrudes from one side of the rotor 22, and a hinge slot 24 ′ having a predetermined length is formed in the hinge arm 24.

In addition, the drive shaft 20 is provided with a swash plate 26 for linear reciprocating movement of the piston (14). The swash plate 26 is formed in a disk shape, and is installed so that the angle with respect to the drive shaft 20 can be changed to change the stroke length for the compression of the working fluid. That is, the swash plate 26 is coupled to the drive shaft 20 so that the swash plate 26 can be changed to be perpendicular to the drive shaft 20 or inclined at a predetermined angle with respect to the drive shaft 20. On one side of the swash plate 26, a connecting arm 28 connected to the hinge arm 24 of the rotor 22 is formed.

The connecting arm 28 and the hinge arm 24 are connected by hinge pins P to rotate in conjunction with each other. Here, the hinge pin P is connected to a hinge slot 24 ′ having a predetermined length of the hinge arm 24, so as to accommodate an angle change of the swash plate 26.

And one side, that is, the front of the piston 14 performing a linear reciprocating motion is formed with a connection portion 18 for connection with the swash plate 26. A pair of hemispherical shoes 19 are installed inside the connecting portion 18, the part of which is open toward the drive shaft 20.

The edge portion of the swash plate 26 is coupled between the shoe 19 of the connecting portion 18. Therefore, when the swash plate 26 having a predetermined inclination rotates and the edge portion thereof passes the shoe 19, the inclination of the swash plate 26 allows the connecting plate 18 having the shoe 19 to be inclined. The piston 14 compresses the refrigerant while linearly reciprocating in the cylinder bore 11.

In this way, the refrigerant compressed in the cylinder bore 11 is discharged to the discharge chamber 53 through the valve assembly 70. When the piston 14 moves to the top dead center (left side in the drawing) in the cylinder bore 11, the internal pressure of the cylinder bore 11 is lowered, so that the refrigerant guided to the suction chamber 51 The gas flows back into the cylinder bore 11 via the valve assembly 70. Through this process, the suction and compression of the refrigerant through the plurality of cylinder bores 11 occurs, and the air conditioner of the vehicle is operated.

Here, it can be seen that the suction chamber 51 and the discharge chamber 53 are partitioned by the partition wall 58. The partition 58 is formed in an approximately circular shape and extends from the bottom of the rear housing toward the cylinder block 10. In addition, an end portion (the left end portion in the drawing) of the partition wall 58 is substantially positioned at a portion corresponding to the cylinder bore 11, and a valve is disposed between the end portion of the partition wall 58 and the cylinder bore 11. The assembly 70 is interposed.

The valve assembly 70 includes a valve plate, a suction and discharge lead valve, and a gasket. Here, the gasket is included to substantially prevent leakage of the refrigerant. However, substantially the end of the partition 58 is formed at the corresponding position of the cylinder bore, so there is no reaction force, so that the end of the partition 58 and the corresponding when the discharge lead valve is opened and closed during operation of the compressor, There is a case in which the airtight state cannot be maintained between the valve assemblies 70. That is, the leakage of the refrigerant occurs at the end of the partition 58 when the compressor operates, which means that the refrigerant flows from the high pressure discharge chamber to the low pressure suction chamber. It is not preferable that such leakage of the refrigerant causes substantial deterioration of the compression performance of the compressor.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned conventional problems, and a main object of the present invention is to provide a compressor capable of preventing leakage of refrigerant in the vicinity of a partition wall partitioning the suction chamber and the discharge chamber.

As described above, preventing the leakage of the refrigerant inside the compressor may be a matter of course in order to obtain a sufficient compression performance of the compressor.

Compressor according to the present invention for achieving the above object is a cylinder block having a plurality of cylinder bores arranged in a circular; A rear housing coupled to the rear of the cylinder block and having a suction chamber and a discharge chamber formed in an area of the cylinder bore and separated by a partition wall; A valve assembly interposed between the rear housing and the cylinder block to move the refrigerant between the suction chamber and the discharge chamber and the cylinder bore based on the pressure difference; And a leakage preventing means provided between the valve assembly and the partition wall to prevent leakage of the refrigerant between the discharge chamber and the suction chamber.

According to the embodiment of the leakage preventing means, a sealing groove formed at an end of the partition wall, and a sealing ring mounted on the sealing groove and in contact with the valve assembly.

Here, the sealing groove is preferably formed at the corner of the discharge chamber side of the partition wall.

According to this invention comprised as mentioned above, the sealing ring is provided in the edge part of a partition, and is in close contact with the valve assembly 170. As shown in FIG. In practice, the sealing ring is kept compressed to some extent by the valve assembly, and has sufficient surface pressure to prevent leakage of the refrigerant. Therefore, even if the valve assembly slightly deforms due to the high pressure in the discharge chamber, the airtight state between the sealing ring and the valve assembly can be sufficiently maintained. Therefore, according to this invention, the leakage of the refrigerant | coolant between a discharge chamber and a suction chamber can be prevented, and the effect which can maintain the compression performance high compression performance sufficiently can be anticipated.

1 is a cross-sectional view showing the configuration of a typical variable displacement swash plate compressor.
Figure 2 is a cross-sectional view showing the configuration of a variable displacement swash plate compressor to which the present invention is applied.
Figure 3 is a perspective view of the rear housing of the variable displacement swash plate compressor to which the present invention is applied.

Hereinafter, the present invention will be described in more detail based on the embodiments shown in the drawings.

As shown, the compressor of the present invention, the cylinder block 110 is provided with a plurality of cylinder bores 112, the front housing is coupled to the front of the cylinder block 110 to form a crank chamber 132 130, and a rear housing 150 coupled to the rear of the cylinder block 110 to form the suction chamber 152 and the discharge chamber 154. The front housing 130, the cylinder block 110, and the rear housing 150 are coupled by a plurality of fastening bolts to form a housing of the compressor as a whole.

A plurality of cylinder bores 112 are radially formed at the cylinder block 110 at regular intervals. The cylinder bore 112 is a portion for compressing the refrigerant. The pistons 114 are respectively accommodated therein, and linearly reciprocate to compress the refrigerant in the cylinder bore 112. One side of the cylinder block 110, that is, the front housing 130 is coupled to the front. The rear side of the front housing 130 is formed concave, in cooperation with the cylinder block 110 to form a crank chamber 132 therein.

The rear housing 150 is installed at the rear of the cylinder block 110, that is, on the opposite side to which the front housing 130 is installed. In the rear housing 150, a suction chamber 152 is formed at the center of the surface facing the cylinder block 110 to suck the refrigerant. The suction chamber 152 serves to deliver the refrigerant to be compressed into the cylinder bore 112.

The rear housing 150 is formed with a discharge chamber 154 through which the refrigerant compressed by the cylinder bore 112 is discharged. The discharge chamber 154 is formed at a portion corresponding to the outer side in the rear housing 153 of the portion corresponding to the cylinder bore 112.

The suction chamber 152 and the discharge chamber 154 are partitioned by the partition wall 155. Substantially the partition wall 155, as can be clearly seen in Figure 3, the rear housing 150 to distinguish the discharge chamber 154 formed in the outer portion and the suction chamber 152 formed in the inner portion, It extends from the bottom of the bottom to the top and is molded. The partition wall 155 is formed in a substantially cylindrical shape.

Between the cylinder block 110 and the rear housing 140, a valve assembly 170 for controlling the flow of the refrigerant between the suction chamber 152 and the discharge chamber 154 is provided. The suction chamber 152 and the discharge chamber 154 are selectively in communication with the cylinder bore 112 by the pressure difference with the cylinder bore 112 to move the refrigerant. At this time, the valve assembly 170 intermittently flows the refrigerant based on the pressure difference between the cylinder bore 112, the suction chamber 152, and the discharge chamber 154.

The driving source for driving the compressor is the driving force transmitted from the engine of the vehicle. The driving force from the engine is transmitted to the drive shaft 120 so that the drive shaft 120 rotates. The drive shaft 120 is coupled to the center bore 116 formed in the rear center of the cylinder block 110 through the shaft hole 133 of the front housing 130, based on the rotational force transmitted from the engine It is rotatably supported.

Inside the crank chamber 132, a substantially disc-shaped rotor 122 is provided in which the drive shaft 120 is coupled to and fixed to the center thereof. The rotor 122 rotates together with the rotation of the drive shaft 120. And the rotational force in the rotating shaft 120 is configured to rotate the swash plate 126 through the rotor 122, and to cooperate with the control valve 180 to change the angle of the swash plate 126, the swash plate ( The configuration that can change the stroke length of the piston 114 by the change of the inclination angle of 126 is substantially the same as described above, and a detailed description thereof will be omitted.

As described above, the suction chamber 152 and the discharge chamber 154 are divided by the partition wall 155 described above. The partition wall 155 is in contact with the valve assembly 170, and the refrigerant is not substantially leaked by the contact with the valve assembly 170. However, there is a fear that a gap occurs between the valve assembly 170 and the end of the partition wall 155 due to the internal pressure of the discharge chamber 154 of high pressure. In order to prevent this, in the present invention, a sealing groove 155a is provided at an end of the partition wall 155, and a sealing ring 156 is provided in the sealing groove 155a.

The sealing ring 156 is formed of a material having excellent sealing ability to seal the gas by being in close contact with the valve assembly 170 such as rubber or silicon. The sealing ring 156 is formed in a ring shape in the same manner as the partition wall 155 to be installed along the end of the partition wall 155.

3 is a perspective view of the rear housing 150 with the sealing ring 156 installed. In the state in which the sealing ring 156 is installed as shown in FIGS. 2 and 3, the sealing ring 156 maintains a slightly protruding state than the end of the partition wall 155. In the state in which the rear housing 150 is coupled to the cylinder block 110, the sealing ring 156 is in contact with the valve assembly 170 to maintain a compressed state to some extent.

As described above, when the sealing ring 156 is in a compressed state, it is natural that the airtightness between the high pressure discharge chamber 154 and the low pressure suction chamber 152 is further improved. For example, even if the valve assembly 170 is elastically deformed to the side of the cylinder bore 122 from the partition wall 155 by the pressure of the discharge chamber 154 of high pressure, the restoring force of the sealing ring 156 is not affected. As a result, the valve assembly 170 may be maintained in a close state without being separated from the valve assembly 170. Therefore, the sealing ring 156 applied in the present invention can sufficiently prevent leakage of the high pressure refrigerant discharged into the discharge chamber 154 to the outside. In addition, this point may be interpreted that sufficient surface pressure is applied between the partition wall 155 and the valve assembly 170 of the portion corresponding to the cylinder bore 112 by interposing the sealing ring 156. It can be said that leakage of refrigerant between the discharge chamber and the suction chamber can be prevented by such sufficient surface pressure.

The sealing groove 155a for installing the sealing ring 156 may be compressed to a certain extent while the sealing ring 156 is in close contact with the valve assembly 170 in an assembled state, thereby maintaining various airtightness. It is natural that branching is possible. In the illustrated embodiment, the sealing groove 155a is formed at the edge of the discharge chamber 154 of the high pressure at the end of the partition wall 155. Since the discharge chamber 154 is a portion where the high-pressure refrigerant is discharged substantially, when the valve assembly 170 elastically deforms, the discharge chamber 154 is deformed from a portion adjacent to the discharge chamber 154 and the leakage of the refrigerant is likely to occur. Therefore, in the present embodiment, the sealing groove 155a and the sealing ring 156 are formed in the corner portion adjacent to the discharge chamber 154 in the partition 155 to prevent leakage of the refrigerant most efficiently. can do.

Looking at the operation of the compressor of the present invention as described above, after the suction in the cylinder bore 112 in the suction chamber 152, the refrigerant compressed by the piston 114 is discharged via the valve assembly 170 Discharged to 154. At this time, the discharge chamber 154 instantaneously maintains a high pressure state, and this high pressure is substantially transmitted to the valve assembly 170. Here, the sealing ring 156 of the present invention is in close contact with the valve assembly 170 by its elastic restoring force even if the valve assembly 170 has a slight elastic deformation to the cylinder bore 112 due to the high pressure. Can be kept sufficiently. Accordingly, leakage of the refrigerant from the high pressure discharge chamber 154 to the low pressure suction chamber 152 may be sufficiently prevented, thereby substantially maximizing the compression efficiency.

In the description of the present invention, the present invention has been described through an embodiment implemented in a variable displacement swash plate compressor. However, the present invention can be applied to any type of compressor in which the suction chamber and the compression chamber are formed in an area corresponding to the inside of the cylinder bore, and the suction chamber and the compression chamber are partitioned by the partition wall.

Within the scope of the basic technical idea of the present invention as described above, other modifications are possible to those skilled in the art, and the protection scope of the present invention is interpreted based on the appended claims. It should also be obvious.

110 ..... Cylinder Block 112 ..... Cylinder Bore
114 ..... Piston 130 ..... Front housing
150 ..... Rear housing 152 ..... Suction chamber
154 ..... discharge chamber 155 ..... bulkhead
155a ..... Sealing groove 156 .... Sealing groove

Claims

A cylinder block 110 in which a plurality of cylinder bores 112 are arranged in a circular shape;
A rear housing 150 coupled to the rear of the cylinder block 110 and having a suction chamber 152 and a discharge chamber 154 separated by a partition wall 155 in an area of the cylinder bore 112;
A valve assembly 170 interposed between the rear housing 150 and the cylinder block 110 to move the refrigerant between the suction chamber and the discharge chamber and the cylinder bore based on the pressure difference;
A sealing groove 155a formed concavely in the corner of the discharge chamber 154 at the end of the partition 155; And
Mounted in the sealing groove 155a is protruded from the end of the partition 155, and is compressed in contact with the valve assembly 170 by the combination of the cylinder block 110 and the rear housing 150. Compressor comprising a sealing ring (156) to maintain the state .

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